CROSS-REFERENCE TO RELATED APPLICATIONS This application claims the benefit of U.S. Provisional Application Ser. Nos. 61/832,522, filed on Jun. 7, 2013, and 61835515, filed on Jun. 14, 2013, the disclosures of which are incorporated herein by reference in their entireties.
BACKGROUND OF THE INVENTION The embodiments described herein generally relate to a vented pressurized gas-powered actuator and methods and structured usable for controlling an actuation force profile of the actuator.
Various types of actuators may be used to automatically move certain portions of vehicles. These actuators may be configured to exert a force within a predetermined range, or to move elements or the vehicle a desired distance or along a predetermined path. Some actuator designs utilize a piston and an attached piston rod powered by a pressurized fluid, such as a pressurized gas. It is desirable to be able to control the force exerted by the actuator according to the position of the piston or piston rod during various portions of the piston rod stroke.
SUMMARY OF THE INVENTION In one aspect of the embodiments described herein, a vented pressurized gas-powered actuator is provided. The actuator includes a housing having a central longitudinal axis and an inner surface. At least one vent groove extends from the inner surface in a direction away from the axis. The at least one groove has a first end spaced apart from a first plane extending perpendicular to the axis, and a second end spaced apart from a second plane extending perpendicular to the axis. The groove second end is closer to the second plane than to the first plane.
In another aspect of the embodiments of the described herein, a vented pressurized gas-powered actuator housing is provided. The housing includes an inner surface and at least one vent groove extending from the inner surface into the wall.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional side view of one embodiment of a vented pressurized gas-powered actuator prior to enabling of gas venting through a vent groove.
FIG. 2 is a cross-sectional side view of the actuator housing shown in FIG. 1 during a portion of piston travel when venting is enabled.
FIG. 3 is a cross-sectional side view of the actuator housing shown in FIG. 1 after the venting period, when gas venting has been disabled.
FIG. 4 is a cross-sectional view of a portion of another actuator including a housing incorporating the vent groove arrangement shown in FIGS. 1-3.
FIG. 4A is a cross-sectional side view of the actuator housing shown in FIG. 4.
FIG. 5 is a cross-sectional end view of a portion of the actuator shown in FIGS. 1-3.
FIG. 6 is a perspective view of the housing shown in FIGS. 1-3.
FIG. 7 is a cross-sectional end view of another embodiment of an actuator housing showing an alternative vent groove arrangement.
FIG. 7A is a schematic view of the actuator housing incorporating the vent groove arrangement shown in FIG. 7.
FIG. 8 is a schematic view of another actuator housing embodiment incorporating an alternative vent groove arrangement.
FIG. 9 is a cross-sectional view of a portion of a housing incorporating an embodiment of a vent groove having a varying cross-sectional area.
FIG. 10 is a cross-sectional view of a portion of a housing incorporating another embodiment of a vent groove having a varying cross-sectional area.
FIG. 11 is a cross-sectional view of a portion of a housing incorporating another embodiment of a vent groove having a varying cross-sectional area.
FIG. 12 is a cross-sectional view of a portion of a housing incorporating another embodiment of a vent groove having a varying cross-sectional area.
FIG. 13 is a cross-sectional view of a portion of a housing incorporating another embodiment of a vent groove having a varying cross-sectional area.
FIG. 14 shows a plot of force exerted by the piston rod vs. displacement of the piston in the negative V direction for the embodiment shown in FIGS. 1-3.
FIG. 15 is a cross-sectional view of a portion of a housing incorporating an exemplary vent groove, showing the basic principle of operation of the embodiments described herein.
FIG. 16 is a schematic view of another actuator housing embodiment incorporating an alternative vent groove arrangement.
FIG. 17 is a schematic view of another actuator housing embodiment incorporating an alternative vent groove arrangement.
FIGS. 18A-C are cross-sectional schematic views showing one embodiment of the progression of formation of a vent groove in a wall of an actuator housing.
FIG. 19A is a cross-sectional side view of a portion of an actuator housing incorporating a vent groove in accordance with another embodiment described herein.
FIG. 19B is a cross-sectional end view of the housing shown in FIG. 19A.
FIG. 20A is a cross-sectional side view of a portion of an actuator housing incorporating a vent groove in accordance with another embodiment described herein.
FIG. 20B is a cross-sectional end view of the housing shown in FIG. 20A.
FIG. 21 is a schematic view of a portion of a pedestrian protection system installed in a vehicle and incorporating a hood-lifting device in accordance with an embodiment described herein.
DETAILED DESCRIPTION Like reference numerals refer to like parts throughout the description of several views of the drawings. In addition, while target values are recited for the dimensions of the various features described herein, it is understood that these values may vary slightly due to such factors as manufacturing tolerances, and also that such variations are within the contemplated scope of the embodiments described herein.
FIGS. 1-20B show various embodiments of a vented pressurized gas-powered actuator, generally designated 10. The actuator 10 may be operatively coupled (via piston rod 50, described in greater detail, below) to any suitable device or mechanism for transmitting a force to the device or mechanism. The actuation force is generated responsive to the introduction of a pressurized gas into a housing of the actuator, in a manner described below. The pressurized gas may be generated within the housing (for example, by a gas generator incorporated into the housing), or the gas may be introduced into the housing from an external gas source in fluid communication with the housing interior. One possible application for an actuator as described herein is in lifting a portion of a hood of an automotive vehicle.
Any of the elements of any embodiment of an actuator described herein may be formed from any suitable material or materials. For example, housing 12 may be formed from a metallic material (for example, stainless steel), a polymer, or any other suitable material or materials.
In the embodiment shown in FIGS. 1-3, actuator 10 has a housing 12, a piston 30 slidably positioned within the housing, and a piston rod 50 attached to the piston so as to move in conjunction with the piston. In the embodiment shown, housing 12 is cylindrical and has an outermost housing wall 12d defining a first end 12a, a second end 12b and a body 12c connecting the first and second ends. Wall 12d also defines a hollow interior 12e of the housing. In the embodiment shown in FIGS. 1-3, housing first end 12a is flared radially outwardly to accommodate a suitable gas generator 14 (for example, a known micro-gas generator) to be inserted and retained therein by crimping, adhesive attachment, or any other suitable method. Alternatively, the gas generator 14 may be attached to housing first end using a suitable retention method. A gas-emitting portion 14a of the gas generator 14 is positioned within the housing so that generated gases flow into the housing interior 12e after activation of the gas generator. If desired, a suitable seal (such as an epoxy seal, o-ring seal or other sealing means; not shown) may be provided to prevent or minimize leakage of generated gas between the gas generator 14 and the housing 12 to an exterior of the housing.
An interior surface 12w of wall 12d has a constant radius measured from housing central longitudinal axis L1 and is structured to permit sliding engagement of a resilient seal 40 therealong, as described in greater detail below. Seal 40 is mounted on a piston 30. In the embodiments shown herein, housing inner surface 12w defines a cylindrical volume, and the vent groove(s) described herein reside outside but adjacent to this cylindrical volume.
In the embodiment shown in FIGS. 1-3, housing second end 12b has an opening 12f structured to receive therethrough a piston rod 50 attached to a piston 30 (described in greater detail below) which is slidably positioned in housing interior 12e. Opening 12f may be sized or otherwise structured to laterally constrain or support to the piston rod 50 as portions of the rod move into and out of the housing through opening 12f. In the particular embodiment shown in FIGS. 1-3, an end wall 12g is formed from a portion of housing 12, and opening 12f is drilled or otherwise formed in the wall 12g. If desired, a reinforcing cap 105 (seen in the embodiment of FIG. 4) may be secured to end 12b of the housing by welding or any other suitable means, to strengthen the housing end against impact forces exerted by the piston 30 contacting the end wall 12g at the end of the piston stroke.
Piston 30 is slidably positioned within housing interior 12e. Referring to FIGS. 1 and 2, piston has a base 30a with an outer wall 30b. A groove 30c is formed in wall 30b and is structured for receiving therein a resilient gas-tight seal 40 (for example, a suitable O-ring). In a known manner, seal 40 resiliently engages or contacts the interior surfaces of housing wall 12d, thereby providing a substantially gas-tight seal between the piston 30 and wall 12d. When piston 30 is positioned in housing 12 with seal 40 contacting the housing wall interior surfaces, the region of contact between the seal and the housing wall defines a boundary between a higher pressure side P1 of the piston and a lower pressure side P2 of the piston. Thus, venting will occur through groove(s) 12v (described in greater detail below) as long as gases traveling along the groove(s) can pass under the seal 40 (between the seal and the housing wall) from the higher pressure side P1 to the lower pressure side P2 side of the piston.
In the embodiment shown in FIGS. 1-3, a projection 30d extends from base 30a. Projection 30d is structure for engaging (or for suitable attachment to) an associated piston rod 50 in an interference fit, or for otherwise enabling or facilitating attachment of the piston rod 50 to the piston 30.
In a particular embodiment, a cavity 30e is formed in piston base 30a. Cavity 30e provides a void space in the piston which is structured to accommodate therein debris or loosened portions of gas generator 14 (for example, petalled portions of the gas generator) resulting from activation of the gas generator and expulsion of the generated gases), and to confine the initial expansion of the generated gases. This can enable a relatively smaller quantity of gas generant to be used in the gas generator to produce a given effect.
Piston rod 50 is the mechanism through which the actuator force is transmitted to an element (for example, a portion of a hood of a vehicle (shown schematically as element 902 in FIG. 21)) connected to the piston rod. Piston rod 50 has a first end 50a attached to the piston so as to move in conjunction with the piston. A second end 50b opposite the first end may be configured for attachment to an element or mechanism to which the actuator force is to be transmitted. In the embodiment shown in FIGS. 1-3, piston rod 50 is hollow. Alternatively, the piston rod may be solid (for example, piston rod 50′ as shown in FIG. 4), or the piston and piston rod may be formed integrally with each other, as a single piece. The piston rod may also have any particular length, diameter, shape and/or other characteristic(s) suitable or necessary for a particular application.
Referring to FIGS. 1-3, at least one vent groove 12v is formed along an inner surface of housing wall 12d. In the embodiment shown in FIGS. 1-3, groove 12v is produced by a forming operation which presses a portion 12x of the wall outwardly, in a direction away from axis L1 and inner wall surface 12w and into the wall thickness, so as to stretch or deform an associated portion of the wall. The groove 12v is formed as the stretched portion 12x of the wall 12d is pushed outward. In the embodiments described herein, the vent grooves (with the exception of embodiments of groove 12k shown in FIGS. 19A-20B) extend parallel to housing longitudinal axis L1.
In the embodiment shown in FIGS. 1-3, groove 12-v has a first end 12v-a spaced apart from a first plane s1 extending perpendicular to the axis L1, and a second end 12v-b spaced apart from a second plane s2 extending perpendicular to the axis. As seen in FIG. 2, groove second end 12v-b is closer to second plane s2 than it is to the first plane s1.
FIGS. 18A-C show the progression of formation of a vent groove 12v starting from an end of housing body portion 12c, using one possible groove formation method. In the embodiment shown, a forming tool 800 is shaped so as to produce a groove having a the desired shape and dimensions, by displacing the material of the housing wall in the direction indicated by arrow W (in a direction away from the housing central axis and into the housing wall) as the tool is inserted into the housing interior from an end thereof in direction V1. The portion 12z of the displaced housing wall material along the exterior of the housing wall flows in direction W and into a cavity C100 of an associated shaping die D100.
In an alternative method of forming a groove or a portion of a groove, the housing 12 is positioned so that its length extends along and rests on a longitudinal base, with a portion of the housing exterior that will reside opposite the internal groove 12v being positioned over a shaping die cavity (such as cavity C100 described above). A press tool is then inserted into an end of the housing. The press tool has a groove-forming portion shaped to produce a groove or groove portion having a desired, shape (including depth and width) and length when the groove forming portion is pressed into the surface of the interior of housing wall 12d. The groove-forming portion of the tool is pressed into the wall 12d in a direction perpendicular to longitudinal axis L1 of the housing 12, thereby forming the groove and deforming a portion of the housing wall outwardly into the shaping die cavity as previously described. Using this method, different portions of the groove can be formed to have different cross-sectional areas along different planes taken through housing 12 perpendicular to axis L1. This enables the cross-sectional area of the portion of the groove through which the gas flows around the seal to be controlled at any point along the groove (as seen for example, in FIGS. 9-13). This method also enables formation of a groove that is spaced from either end of the housing 12.
In another alternative method, groove 12v is formed by a broaching operation performed on the housing wall interior surface. In a known manner, the broaching operation removes a desired amount of material from the wall interior surface, thereby reducing the thickness t of the housing wall opposite the groove.
In another alternative method of forming a groove or a portion of a groove, housing 12 is formed from a suitable polymer. Any of grooves 12v may be formed by one of the methods previously described, or the groove(s) may be formed, for example, by molding an insert fabricated into a desired groove profile shape (for example, one of the groove shapes shown herein) into a wall of the polymeric housing. The insert may then be removed from the groove formed into the housing wall after the molded housing has cooled to a sufficient degree.
FIG. 15 is a cross-sectional view of a portion of a housing incorporating a vent groove 12v′ in accordance with an embodiment described herein, showing the basic principle of operation of the groove. The drawing shows piston-mounted seal 40 progressing in direction V along surface 12w from its pre-activation position, after activation. In position 1, the seal has not yet reached the groove 12v′. Thus gases on higher pressure side P1 are prevented by the seal from reaching the lower pressure side P2 of the piston by contact between the seal and the housing wall inner surface 12w. In position 2, after the seal 40 has passed end 12v′-a of groove 12v′, the gases on the P1 side of the piston have a route along the groove and around the seal to the lower pressure side P2 of the piston. The gases continue to flow along the vent groove 12v′ as shown by arrow Z, until the seal reaches groove end 12v′-b. In position 3 of the seal, the seal has passed groove end 12v′-b, the groove no longer resides below or outside of the seal. Thus, the gas flow path through the groove is blocked.
The fluid flow rate along the groove (and thus, the actuator force profile) is controlled by controlling the cross-sectional dimensions of the groove ends and the portions of the groove between the ends. These parameters may be varied at various locations along the groove as described herein, in order to achieve a desired force profile.
The actuator force profile (defined herein as the force exerted by the piston rod 50 on an element connected thereto as a function of time) may be controlled by controlling structural features of the actuator, such as the number of vent grooves, the areas of the vent groove(s) (defined for each vent groove as the area bounded by the seal 40 sliding over the groove and the portion of the housing wall 12d defining the edge of the groove at any given cross-section of the housing, shown, for example, as area A in FIG. 5), the length(s) of the vent grooves, the gas output characteristics of the gas generator, and other pertinent factors. The dimensions of these features can be modified to control such characteristics as the total flow rate of gases along the vent grooves and the amount of time venting is enabled.
For example, in the embodiment shown in FIGS. 1-3, as groove 12v extends outside or beyond remainder of the housing wall interior surface, the groove 12v provides a flow path (or vent) for pressurized gases past the seal 40, from the higher pressure side P1 to the lower pressure side P2, when the seal is positioned over the vent groove as shown in FIG. 2. Gases flowing along the groove 12v to the lower pressure side of the piston 30 are then free to flow out of the housing through housing opening 12f.
Venting through a portion of the groove is enabled under seal as long as the groove extends to both the higher pressure side P1 of the seal 40 and the lower pressure side P2 of the seal. Stated another way, in the embodiments described herein, venting along a groove will be enabled as long as a gas flow passage exists along the groove and past the seal 40, from the higher pressure piston side P1 to the lower pressure side P2.
In embodiments described herein, the length and position of a vent groove may be specified such that the venting is enabled along only a portion of the stroke length of the piston. In such embodiments, flow of a portion of the generated gases along the vent and past seal 40 would be enabled only for a portion of the piston stroke corresponding to the length and position of the vent groove. In other embodiments of the groove, the length and position of a vent groove may be specified such that the venting is enabled along the entire length of the constant internal radius portion of the housing (i.e., along basically the entire stroke length of the piston).
In particular embodiments, the positions of the ends of a groove (or grooves) may be specified so as to control the point in the piston stroke at which the onset and/or end of venting occurs. For example, the actuator housing embodiment shown in FIGS. 1-3 includes a groove 12v structured to enable venting to commence at a point 12v-a reached by the piston after travelling a specified distance within the housing. After the piston reaches groove 12v at 12v-a, venting is enabled through the groove until the seal passes 12v-b, which is the end of groove 12v.
FIG. 4A shows a particular embodiment of the housing shown in FIG. 4. In this embodiment, the groove 12′v is formed along the length of the housing such that groove end 12′v-b resides at a distance D1 of 30 millimeters from an interior surface of housing end wall 12′g (which defines plane s2 in this embodiment), and groove end 12′v-a is located at a distance D2 of 30 millimeters from plane s1.
In the embodiment shown in FIGS. 1-3 and FIG. 15, a single groove 12v is incorporated into the housing. Venting is delayed until the piston reaches groove 12v at 12v-a, and then is enabled all the way until the piston reaches 12v-b, at an opposite end of the groove.
In other embodiments, multiple vent grooves may be spaced apart along the housing wall interior surface. For example, FIGS. 7, 7A, 16 and 17 show schematic views of actuator housings having multiple spaced apart grooves, 12v-1 and 12v-2. Planes s1 and s2 schematically represent the longitudinal ends or limits of the constant radius portions of the housing interior surface 12w, along which venting from the higher pressure piston side P1 to the lower pressure side P2 may be enabled by providing vent grooves along the housing. That is, inner surface 12w (except for the portions along the vent grooves) is located at a constant radius from axis L1 between planes s1 and s2. The piston moves in direction V, with the piston stroke beginning at or about plane s1 and ending at or about plane s2.
FIG. 7 shows a plan cross-sectional view of a portion of an actuator housing having two diametrically opposed vent grooves 12v-1 and 12v-2 (i.e., second groove 12v-2 is formed into housing wall 12d diametrically opposite a first groove 12v-1). FIG. 7A shows a schematic view of a housing incorporating the vent groove arrangement shown in FIG. 7. In the particular embodiment shown in FIG. 7A, grooves 12v-1 and 12v-2 have equal lengths and are coextensive along the housing (the beginnings of the grooves are located along a common plane s3 extending perpendicular to the housing longitudinal axis L1, and the ends of the grooves are located along another common plane s4 extending perpendicular to the housing longitudinal axis L1 and located spaced apart from the first plane). Thus, in this embodiment, venting through both grooves commences at the same time and ends at the same time as the piston travels in direction V. In addition, first groove 12v-1 has a first end 12v-1a spaced apart from plane s1 and a second end 12v-1b spaced apart from plane s2. Second groove 12v-2 has a first end 12v-2a spaced apart from plane s1 and a second end 12v-2b spaced apart from plane s2. It is also seen that second groove second end is closer to second plane s2 than it is to first plane s1.
Referring to FIG. 8, in another particular embodiment, a second groove 12v-2 has a first end 12v-2a intersecting first plane s1 and a second end 12v-2b intersecting the second plane s2. Thus, venting is enabled along groove 12v-2 during essentially the entire stroke of the piston along housing inner surface 12w. Also, venting is enabled along groove 12v-1 while the seal 40 travels between a plane s3 and a plane s4. Planes s3 and s4 extend perpendicular to axis L1 and are located between planes s1 and s2.
In any embodiment incorporating multiple grooves, each groove may have any desired length and relative position along the length of housing 12. That is, the grooves may or may not have the same lengths, and may or may not be coextensive with each other, according to the actuation force requirements of a particular application. Also, any desired number of vent grooves may be employed. In addition, although the grooves 12v-1 and 12v-2 are angularly spaced apart 180°, the angular spacing(s) and/or other distances between any pair of grooves in any set of grooves may be equal or unequal.
Another embodiment (shown in FIG. 16) includes at least two grooves 12v-1 and 12v-2 with overlapping ends. Thus, in the embodiment shown in FIG. 16, a portion of first groove 12v-1 extends between a third plane s3 and a fourth plane s4, located between the first and second planes s1 and s2 and extending perpendicular to axis L1. Also, a portion of second groove 12v-2 extends between the third and fourth planes. Groove 12v-1 is structured to enable venting to commence at a point 12v-1a reached by the piston after travelling a specified distance within the housing. After the piston reaches groove 12v-1 at 12v-1a, venting is enabled through the groove 12v-1 until the seal passes 12v-1b, which is the end of groove 12v-1 and resides along plane s3. However, during passage of the seal from point 12v-1a to 12v-1b along groove 12v-1, the seal passes over point 12v-2a (located along plane s4, at the first or lower end of groove 12v-2), thereby enabling venting along groove 12v-2 as well as through groove 12v-1. Venting is now enabled along both grooves until the seal passes point 12v-1b along groove 12v-1, after which venting is enabled only along groove 12v-2 until the end 12v-2b of this groove.
Although FIG. 16 shows an the embodiment having one pair of overlapping grooves, any number of overlapping grooves may be employed as needed to achieve a desired actuation force profile. For example, a single first groove enabling venting during a first portion of the piston stroke may overlap with multiple second grooves, in the manner shown in FIG. 16, to enable venting through these second grooves in a later portion of the piston stroke. Similarly, multiple first grooves enabling venting during a first portion of the piston stroke may overlap with a single second groove, in the manner shown in FIG. 16, to enable venting through this second groove in a later portion of the piston stroke.
Another embodiment (shown in FIG. 17) includes at least two grooves 12v-1 and 12v-2 arranged along a common plane X′ passing through and extending parallel to central axis L1, with a space D′ between adjacent ends 12v-1b and 12v-2a of the grooves. Longitudinal axes of both grooves lie along the plane X′ which extends from the housing longitudinal axis L1 to a side of the housing, as shown in FIG. 17. Groove 12v-1 is structured to enable venting through this groove to commence at a point 12v-1a reached by the piston after travelling a specified distance within the housing. After the piston reaches groove 12v-1 at 12v-1a, venting is enabled through the groove until the seal passes 12v-1b, which is the end of groove 12v-1 and is located along a plane s3 extending perpendicular to axis L1. Venting is then disabled until the seal reaches end 12v-2a of groove 12v-2, located along a plane s4 extending perpendicular to axis L1. Venting is then enabled along groove 12v-2 until end 12v-2b of groove 12v-2 is reached.
In the embodiment shown in FIGS. 1-3, groove 12v has a constant cross-sectional area (within the limits of manufacturing tolerances) along its entire length. In any of the embodiments described herein, the grooves (where multiple grooves are incorporated into the housing) may have the same cross-sectional areas or different cross-sectional areas.
In addition, the cross-sectional area of any particular groove may be varied along its length as another means of affecting the actuator force profile. Control of the area through which the gases may flow enables a controlled variation of the gas flow or venting rate as the piston travels along the groove.
For example, in the embodiment shown in FIG. 9, the depth d′ of groove 112v varies along the length of the groove. This variation in groove depth d′ produces a corresponding variation in groove cross-sectional area along the length of the groove. In the embodiment shown in FIG. 9, the groove 112v is tapered so that the depth d′ of the groove varies at a uniform rate along the length of the groove. However the cross-sectional area of the groove can be varied in any desired manner that can be fabricated.
In addition (or alternatively), the forming tool may be formed so as to vary the width of the tool therealong. This enables the width of a groove formed in the housing wall to be correspondingly varied during fabrication of the housing.
In other embodiments, any groove may be formed into adjacent portions or sections into “zones” having different characteristics.
For example, in the embodiments shown in FIGS. 10 and 11, a first portion R1 of the groove 112v has a constant cross-sectional area, and a second portion R2 of the groove adjacent the first portion has a cross-sectional area which varies along the length of the groove.
In the embodiment shown in FIG. 12, a first portion R1 of the groove 112v has a first constant cross-sectional area, and a second portion R2 of the groove adjacent the first portion has a second constant cross-sectional area different from the first cross-sectional area.
In the embodiment shown in FIG. 13, a first portion R1 of the groove 112v has a cross-sectional area which varies along the length of the groove, and a second portion R2 of the groove has a cross-sectional area which varies along the length of the groove.
In view of the above, it may be seen that numerous options exist for providing any of a wide variety of actuator force profiles, using the methods and structures described herein.
During operation of the actuator, the gas generator or other pressurized gas source is activated to introduce pressurized gas into the housing on the higher-pressure side P1 of the piston. The pressurized gas forces the piston in direction V, whereby a force is exerted by piston rod 50 on an element or mechanism attached thereto. The actuator force profile will be related to the amount of pressurized gas vented through the groove(s) from the higher pressure side P1 of the piston to the lower pressure side P2. At the end of the piston stroke and/or when the resilient seal has passed the groove(s) and is in flush contact with ungrooved surfaces of the housing wall, the gasses remaining in the higher pressure side can continue to escape to some degree from the higher-pressure area to the lower pressure area between the housing wall and the resilient seal until the pressure in the higher-pressure area is nearly equalized with atmospheric pressure. The result is a fully depressurized actuator within seconds of actuator deployment.
Also, in a particular embodiment, prior to activation of the actuator, the piston 30 is positioned such that a portion of at least one vent groove resides on both the higher pressure side P1 (i.e., the gas generator side) and the lower pressure side (i.e., the side of the piston on which the piston rod 50 exits the housing 12) of the resilient seal 40. This enables the housing internal pressures on sides P1 and P2 of the piston to be equalized during assembly of the actuator and prior to actuator activation.
FIG. 14 shows a plot of force exerted by the piston rod vs. displacement of the piston in the negative V direction in the drawing for the embodiment shown in FIGS. 1-3, after the actuator has been fully deployed (i.e., at maximum travel of the piston). As seen from FIG. 14, as the piston rod 50 is pressed back into the housing, the force resisting displacement of the piston 30 in the −V direction steadily increases until the piston resilient seal 40 reaches a point just past point 12v-b along the groove 12v. At this point, venting of the pressurized gas stored on side P1 of the piston is once again enabled. The gas vents through groove 12v, thereby causing the rapid drop in force resisting further movement of the piston in the −V as direction shown in FIG. 14.
Referring now to FIGS. 19A-20B, in another embodiment 12k of a vent groove, the length of the groove extends along an axis K residing on a plane that is perpendicular to housing axis L1. The cross-sectional dimensions of the groove may be controlled to provide a relatively rapid or “pulsed” release of gas of a desired amount, from high pressure side P1 to lower pressure side P2, as the seal 40 passes over the groove. The groove 12k may extend along 360 degrees of the surface of wall 12w, thereby forming a continuous “ring”, as shown in FIGS. 20A and 20B. Alternatively, the groove 12k may extend along only a specific portion or included angular extent M of the surface 12w, as shown in FIGS. 19A and 19B. These variations enable increased flexibility in control of the actuator force profile. The groove 12k may be formed using one of the groove formation methods described herein.
FIG. 21 is a schematic view of a portion of a pedestrian protection system 900 installed in a vehicle 880 and incorporating a hood-lifting device 10 in accordance with an embodiment described herein. In this embodiment of the pedestrian protection system 900, a vehicle mounted sensor 810 detects contact between the vehicle and a pedestrian (not shown). Responsive to this detected contact, an activation signal is sent to the hood-lifting mechanism 10, resulting in activation of the gas generator or otherwise releasing pressurized gases into the interior of housing 12 to produce extension of the piston rod 50 from the housing, as previously described. The extending piston rod 50 then raises the portion of the hood 902. The hood-lifter activation signal may be sent from the sensor 810 or from a suitably-configured controller (not shown) which receives the vehicle-pedestrian contact signal from sensor 810 and generates the activation signal in response thereto.
It will be understood that the foregoing descriptions of the various embodiments are for illustrative purposes only. As such, the various structural and operational features herein disclosed are susceptible to a number of modifications, none of which departs from the scope of the appended claims.
